Pneumatic-turbine drill.



R. A. NORLING. PNEUMATIG TURBINE DRILL.

APPLICATION FILED SEPT. 18,1913. 1)()99392 Patented June 9, 1914 s SHEETS-snm R. A. NORLING.

PNEUMATIG TURBINE DRILL.

APPLIUATION FILED sBPT.1a.1Q1a.

1,099,392. Patented June 9, 1914.

3 SHEETS-SHEET 2.

R. A, NORLING. BVNEUMATIO TURBINE DRILL. APPLICATION FILED SEPT. 18,1913.

1,09992` Patented June 9,1914 HjIBTB-BHEBT 3.

r e, r 4v /C I /yaZg/y A? Jj@ E i? si y 36d i A y m 1| l mi 1 l y i UMTED STATE@ PATENT OFNQE,

REINHOLIP A. NOBLING, OF AURORA, ILLINOIS, ASSIGNOR T6' AURORA AUTOMATIC MACHINERY COMPANY, OF AURORA, ILLINOIS, A CORPORATION OF ILLINOIS.

PNEUMATIC-TURBINE DRILL.

Specification of Letters Patent.

Patented June 9, 1914.

Application led September 18, 1913. Serial N o. 790,575.

T0 all 07mmj 'it may concem Be it known that I, Reunion) A. NonLiNG, a citizen of the United States. and a resident of Aurora, in the county ot' Kane and State of Illinois, have invented certain new and useful Improvements' in Pneumatic- Turbine Drills; and l do hereby declare that the following is a full, clear, and exact description thereof, reference being had to the accompanying drawings, and to the letters of reference marked thereon, which form a part ot' this specification.

This invention relates to improvements in pneumatic turbine drills and more particu larly to an improved construction for a pneumatic turbine motor adapted to operate a drilling or like tool.

In the construction of a drilling tool ein bodying my invention, it is proposed to produce a highly efficient and durable tool ot' exceptional power and extreme lightness of weight. To gain this end, l provide a high speed turbine rotor mounted in suitable auti- 't'rietion bearings, a proper tool -holding spindle,and speed reducing and power transmission interposed between the rotor and tool spindle, so constructed and arranged as to allord perfect ruiming balance in all parts, thus elin'iinating to a large extent the loss oi' power b v friction. In addition, I propose to provide a controlling means particularlvr designed with a view to alording perfect ease and convenience in the manipulation of the tool, and the most efficient utilization of the power at hand.

My invention consists ot the futures hereinafter i'ully described and more particularly pointed out in the appended claims.

ln the accompanying drawings Figure l is a longitudinal section of the drill embodying my invention; Fig. 2 is a view in elevation of the drill with a portion of the gear casing brolteu away and parts therein shown in section; Fig. 3 is a detailed view in eleva tion ot the spindle removed from the casing, showing the construction of the same; Fig. -l is a. cross-sectional view, taken on line left of Fig. l; Fig. 5 is a cross-sectional view, taken on line 5-5 of Fig. 1; Fig. G is a view in ciosssection, taken ou line G-G ot Fig. l; Fig. 7 is a view in cross-section, taken on line TNT of Fig. 2, showing the (.:onstruetion of the controllingr lever for the throttle valve; Fig, 8 is a cross-sectional View, taken on line 8-8 of Fig. 7 showing the structure of the throttle valve.

Referring to the drawings: The device embodying my invention comprises in the main the combination of elements as follows, to wit;-a rotor casing l, within which is formed the nir inlet passages, nozzles, and rotor chamber 1, the latter containing the rotor or turbine wheel 2, a gear casing 3, con'- taining the rotatable tool spindle 4 which carries a train of speed reducing or rcduction gears interposed between the turbine shaft 5 and fixed internal gear G at the lower part of the gear casing; a spindle support 7, separating' the rotor chamber aud the gear casing; a threaded collar 8 engag ing the adjacent marginal flanges of said rotor casing 1 and the gear rasing 2, a handle 9 secured to the upper portion of the rotor casing, and a throttle valve mechanism l0 mounted within the rotor casing.

Referring now more in detail to the construction of `the above named elements. The rotor or turbine wheel 2 is rigidly Secured to the turbine shaft 5 adjacent toits upper extremity, said wheel being provided with a tapered bore which engages a similarly tapered portion 5 of the shaft. A washer 11 is mounted upon thc shaft and bears against the turbine wheel, the same being interposed between said turbine wheel and a nut 12 eugagiug a threaded portion of the shaft and bearing against the said washer. The said rotor is adapted to turn within the beforenientioned rotor chamber l formed in the lower portion of the rotor casing 1. The periphery of the rotor is provided with a pluralitfv of radially arranged and evenly spared peripheral blades or buckets 2 (Figs. l and 4), the said blades being provided with uniformly concaved surfaces 2l each or' which is adapted to receive an impulse from jets of the motive fluid directed against them, in a manner hereinafter to be described.

The upper extremity of the turbine shaft is reduced in size and is mounted within an anti-friction roller bearing which rests within an axial bore in the top or end portion of the rotor easing, and is constructed as `follows: A plurality of rollers i3 (Fig. l) are held within a retaining cage 13, said rollers and cage surrounding the shaft. A bushing 14 fits within the axial bore 1b and neloses the said roller bearing, the said bushing acting as a bearing surface for the rollers .13. The bearing cage and bushing abut at their ends against a thrust plate 15 and a thrust block 16, the said-thrust plate resting upon thev shoulder 1c formed at'the base of the said bore 1b and vthe said thrust block resting loosely in the upper portion of said bore. The. thrust block is held in place by the handle 9, the base plate 9a of which covers' the entire upper surface of the rotor casing, and through which extend bolts 9"v which are anchored in the rotor casing.

Lubrication is supplied to the roller bearing by means of an annular channel 17 which surrounds the bushing 14 and communicates 'with an oil hole 17a extending through the wall of the rotor casing. A screw plug 18 engages the oil hole and is adapted to be screwed inward,thus forcing a small quantity of grease which is contained in the said oil hole 17'a and the channel 17 into the bearing, through a plurality of apertures 14a in the bushing 14. Within the gear casing 3 and surrounding the turbine shaft 5 is rotatably mounted the before mentioned tool spindle 4 which is constructed as follows: Two spindle disks 19 and 20 ale rigidly secured together and at consid. erabledistance apart, by means of a spindle sleeve 21 the ends of which fit within annular channels forced in the adjacent peripheral margins of the disks, by means of bolts 22 (Fig. 3) extending through the disks at points diametrically opposite each other, and adjacent to the peripheries of the disks and to the inner'surlaceof the spindle sleeve. The upper spindle disk is provided with an upwardly extending bearing flange .19 (Fig. 1), which forms a continuation of a central bore of the said disk through which extends the turbine shaft 5. bearing flange 19a engages an anti-friction bearing 23 mounted within the spindle bearing support 7. The said bearing support `comprises an annular disk the margin ot which is mounted within grooves formed in the adjacent inner margins of the gear case and rotor case and rigidly held in position by the threaded collar 8, which acts to clamp the said bearing support in place as Well as to connect the said rotor and gear casings. The said roller bearing 23 rests within an annular space formed within an en largcd central portion ot the said bearing support, and comprises a bushing Q4 sur rounding a plurality of rollers Q5 which 'bear against the outer and inner surfaces of the bearing flange and the bushing, respectively, and a hearing thrust plate 24 held in thel upper portion of the depression. The rollers 25 are. each provided with an annular peripheral groove y25 adapted'to admit and engage an annular wire bander retaining collar QG closely surrounding the The said flange or journal 19a, said wire band being adapted to retain the rollers in place when the spindle is removed from the bearing. The lower ends of therollers rest upon the spindle thrust bearing plate 27 which is fitted, within an annular space immediately below the roller bearing 28 and held from movement by means of a shoulder 7 formed in the bearing support. Immediately below the said plate 27 is an annular bearing retainer 28 forming a circular ball race or groove containing a series of bearing balls 28a arranged in a circle between the members 27 and 19 and surrounding the spindle' 25. The said bearing retainer is mounted within a Space separating the upper surface of the spindle disk 19 and the adjacent surface of the spindle bearing support 7, there being grooved ball races formed in said upper surfaceof Said spindle disk andA in the thrust plate 27, which are engaged by the bearing balls EZSX Integral with or iiXed to the lower spindle disk 20 and in axial alinement with the turbine shaft is a spindle sleeve 29 (Figs. 1 and' 2), the same consisting of a tulmlar shaft extending downwardly from the central portion of said disk and throughaiid beyond the lower extremity of the gear casing (Fig. 1). The said spindle sleeve 29 is provided with a roller bearing 30 (Fig. 1) comprising peripherally grooved .rollers 30 surrounding the spindle sleeve at substantially its central portion and' having' an annular collar `or wire guide 30b in engagement with the grooves, a bushing 30 surrounding the rollers 30 and fixed within an annular space formed in thelower portion of the gear easing adjacent to its extremity,`and two thrust plates 30d, 30d surrounding the spindle sleeve at the ends of the rollers 30a and between which the same are located. This bearing is very similar in construction to the upper spindle bearing and hence need not be further described. Upon the surface of the spindle sleeve and immediately above the spindle bearing, is formed an annular collar 29 having a downwardly facing surface adapted to engage the upwardly facing surface of the adjacent thrust plate 30Ll of the bearing 30, and acting to limit the endwise movement of the spindle. At the lower extremity of the gear casing through which extends the spindle sleeve is provided a stuit ing box 31 surrounding the said sleeve and in screw-threaded engagement with an internally threaded portion of the gear casing 2l. 'lhe stuffing box retains within an annular space a packing ring 31, its purpose being to insure a tight joint between the spindle sleeve and the gear casing and to thereby prevent the escape of oil from the said gear easing. 'As above indicated, the said spindleI sleeveis provided with an axial bore of substantially uniform diameter extending lli fill

titi

mensen its entire length and through the lower disk 2l). l/Vithin the said bore is held asocket member 32, the same being` provided at its inner end with diametrieally arranged grooves 32 (Figs. l and 6) extending lon- :zitudinally of said socket lmember and adapted to engage similarly arranged projections 29? formed on the inner surfaceof the spindle sleeve 29. The outer extremity of the tool socket 32 is provided with a flange 32" which abuts against the end of the spindle sleeve 29. A lock nut or cap 32C extends over the end of the socket sleeve and the flange B2b and engages the threaded extremity of the spindle sleeve 29, said nut actingr to hold the socket sleeve 32 within the spindle sleeve, A'andlby its removal to permit the withdrawal of the said socket sleeve. The socket of the sleeve 32 is slightly tapered to conform with the like taper-of the shank of the tools to be held therein.

The central bore of the spindle sleeve by preference extends upwardly through the disk 2O and within the upper portion of the boro is mounted the bearing,` for the lower end of the turbine shaft, said 'bearing comprising a plurality ,of cylindric rollers 33.

mounted Within a retainingl cage 33% The retaining cage rests upon a thrust plate 3ft for the lower end of the turbine shaft, said plate being held from movement by its engagement with a retaining` shoulder formed in said bore. 'lhe thrust plate 34 also acts to hold the rotor shaft bearing in place. 4

Referring now to the construction andv arrangement of the gears which are carried by the spindle and which transmit rotative movement from the turbine shaft to the spindle: thesame comprises two sets of speed reducing gear wheels' each set consisting of two identical gear spindles 35, 35 and klo, 36 mounted Within .the hollow tool spindle and ,arranged diametrically opposite each other on either side of the axis of thel turbine shaft. Referring first to the gea-r spindles 35, 35 (Figs. 2 and 5), the same constitute the tinst set of reduction gears and comprise spur gea-r wheels 35, `35a which mesh with a central spur pinion 37 formed upon the surface of or fixed to the turbine shaft 5. 'lhc axes of these gears are parallel with that: of said turbineshaft. lm-

ymediately below the large spur gear wheels are smaller pinions 35i', 35 integral therewith. .The gears 35 are provided with .iifuirnals or stub shafts 35C which engage anti-friction roller bearings 38 and 39 mounted within annular recesses formed in the upper and lower spindle disks i9 and 20,'

respectively; Meshing with the pinions 35 of the gear spindles 35., are the gearl wheels 36 on the gear spindles 256k lfig. 1) constitutingthe second set of reduction gears. rlhe gear wheels 36 lie in the plane of the pinions 35 and below the plane of the near wheels 35a. rl`he stub shafts 30C, 36 of the gear spindles ll, 36 are mounted at their upper ends in anti-friction bearings 40, 4() located in the upper spindle disk 19. The portions of the said gear spindles ll, 36 below the spur gear wheels 36, however, arev of a somewhat greater diameter than the stub shafts .'flilc and extend downwardly through and beyond the lower spindle disk 20, the portions thereof below said disks having pinions :lob cut upon their surfaces. (See Figs. l and (i.) The said pinions 361 mesh with the stationary internal gear li sccurci'l within the L i-ear. casing, immediately below the lower spindle disk Q0. Roller bearings 4l, lil are mounted within the lower spindle disk and engage the bearing surfaces 36d, 36 of the portions of the gear spindles 36, lo between the spur gear wheels 36, 36 and thc pinions 36h, 36h. `In order to afford sullicient space to accommodate the large spur gear wheels B5, 35 and 36, 36a of the said gear spindles and portions of the spindle sleeve S21 are eut away, as shown at 42, i2 of Figs. l, 2 and 5. The adjacent faces of the upper and lower spindle disks 19 and 20 are preferably provided with washers 43 and 44, respectively, the same acting to retain the several bearings in position.

.llhe manner in which. the power is transmitted from the rotor shaft to the tool spindle, by means of the arrangement of the said reduction gears, may. be understood from the following: The rotation of the turbine shaft which is turning at a high rate of speed is first transmitted to the gear spin.- dles 35, 35 constituting the first set of reduction gears, by the intermeshing of the large gear wheels 35, 35 with the turbine shaft pinion 3T. (t'iee Figs. 1,' 2 and' 5.) From the Vgear spindles 35, 35, the rotative movement is transmitted to the gear spindles 3G, 3G by the intel-meshing' of the gear wheels 36 and the pinions 35, the speed ot' rotation of the gear spindles 3G, 3G being substantially reduced by reason' of the ditference in the size of the said gear wheels 36, 3G and pinions 35h, 35". The rotative movement thus transmitted to the gear spindles Bo, 3G, nets to rotate the entire spindle el, by reason of the intermeshinn' of the pinions 3o", 3G of the gear spindles 3G, 3G and the stationary internal gear ti. (See Figs. 1, 5 and (S. llrom this description, it is readily o served that the :form of power transmission embodied in my invention partakes of the nature of a plan' etary drive and by the successivo reductions in speed` of the tool spindle is suitable for the operation of the drillingr tools carried thereby. y

The air is supplied to the rotor by the following means: The upper portion of the Ntwo annular channels 5,0, 51 by means of nels 50 and 51 are separated by a partitionl rotor, rotating the same in the two downwardly inclined passages 52 and 53,l respectively, at the upper ends of which is located the throttlevalve 10. (See Fig. 1.) The air channels 51, 52 are preferably formed by cutting grooves in a portion of the casing of increased thickness of metal surrounding the rotor and lit-ting a ring 54 over the grooves, thereby converting the same into the said channels. The ring 54 is preferably provided with apertures comp* v'municating with each. of the channels 50 Y 25 and 51, and which are normally closed by means of screws 55, 55, havingscrew-thread )ed engagement therewith. By removing these screws, any particles of dirt which may have become lodged within the air channels may be blown out by admitting air through the throttle valve. Thechanwall 56within which are formed a plurality of small air passages or nozzles 57 and 58 (Fig. 4). The nozzles or tangential passages 57 and 58 lie in a plane perpendicular tothe axis of the rotorshaft and are in tangential relation to the rotor'or at oblique angles with respect to the radii of the rotor. As illustrated in the drawings, the said nozzles are arranged in two series of nozzles spaced at angles of 90 #about the rotor casing. One of said series consists of lfour -nozzles 57, which communicate with the channel 51 by means of short vertical channels 57a formed at the outer ends of the nozzles, These nozzles are inclined in the direction of the normal direction of rotation of the rotor l tangentially with respect to the periphely e the rotor. Thus a stream of motive directed through the nozzles 57, strikes the concaved lfaces 2b of the buckets 2 of the roper direction for operating fthe tool, Ihe other of said sets of nozzles 58 are spaced in similar relation about the rotor casing,

` each -of the nozzles being located adjacent 'to a nozzle 57. Said nozzles 58, 58 are connected with the channel 50,' by means of verp tical passa-ges 58EL (Fig. 1) at the 'outer' ends thereof, and are also inclined tangentially with-respect to the tangent to the periphery of the rotor but in aireverse direction from the inclination of the nozzles 57.' Thus streams of air from the nozzles 58 will throughout substantia ly one-half the circumference of the rotor casing.

The throttle valve 10 before mentioned as located at the upper ends of the air passages 52, 53 and interposed between the said passages and the annular air passage 46, com prises the following elements: A cylindric valve chamber 10 is formed integral with the rotor casing and within which is tightly fitted a Valve bushing 61 provided with a plurality of ports as follows: A. large port 61(Fig. 1) located in the upper portion thereof and communicating with the air passage 46, and two smaller ports 61b and 61 located diametrically opposlte said port 61. Theports 61b and 61are spaced a short. distance apart circumferentially and are`;elonters with a'similarly elongated recess 52a (Figs. 1 'and 2), forming the upper -ex-y tremity of the' inclined air passage 52, and the other po-rt 61 in like manner `communicating with the-elongated recess 53 of the air passage 53. Within the bushing 61 is rotatably mounted the cylindric valve member 62 provided witha lpassage 63 extending diametrically through the 4central portion thereof. The said passage 63 is adapted t0v constantly register with the port 61 of the valve bushing 61 at one extremity and with either of the ports 61b or 61 at its other eX- tremity, said latter extremity beingprovided with a llongitudinally elongated mouth 63 (Fig. 2) to correspond with the shape of the ports 61b and 61. The ,valve member 62 (Fig. 8) is provided at one end with afstem 62 extendin through and beyond the-end wall of the ushing 61. Within the other end of the bushing is screwed a valve plu 64 provided at its inner vend with a centra depression 6414 within ,which is retained a spring 65 bearingagainst the adjacent end ofthe valve member 61 and acting'to force the said valve member tightly against the seat formed by the end wa l of the bushing, thereby'preventing a leakage of the motive fluid. Rigidly `mounted, upon the stem 62 ofthe valve isthe throttle lever 66 extending outwardly from the tool immediately below f gated in form. One of said ports 61 Aregis- 6l", 61 of the valve bushing, to wit: an open, a closed and a reversed position. When the lever is in the open position, the following conditions exist: The valve 1nember 62 is in such a position that the passage 63 connects the main air passage 116 with the inclined air passage 52. Thus the motive fiuid under pressure being admitted to the main air passage through the inlet connection 48, is carried through the valve and the air passage 52 into the lower channel'l, and thence through the nozzles 57, communicating with the said channel 51, and against the concaved faces of the rotor blades orbuckets 2", the force of the streams of air issuing from the several nozzles 57 effecting the r'o tation of the rotor and turbine shaft at a high rate of speed, the direction of rotation,

of the rotor under the above described conditions being the proper one for operating the drill.

The closed position of the lever corresponds to the position of the valve member in which the passage 63 thereof reofisters at its lower end with a portion of the metal wall of the bushing 61 lying between the ports 61b and 61C. Obviously in this position the air is entirely cut oil".

The reversed position of the lever corresponds to the position of the valve in which the passage 63 connects the main air passage 46 and the port 61" of the valve bushing, thus the air is free to pass into the inclined air passage 53 which communicates with the upper air channel 5() and thence through the nozzles 58. The air issuing from said nozzles 58 strikes the rotor blades upon their convex surfaces, thus retarding the rotation ofthe turbine or rotor effecting' the rotation of' the turbine rotor and shaft in the reverse direction, that is, in the opposite direction from that produced .by the air issuing from the nozzles 57, under which circumstances the lever is in the open position.

It is at once apparent that the driving effect or the power transmitted to the rotor is very muchless when the rotor is moving in the reverse or backward direction than when it is running in the proper or forward direction, due to the fact that the air strikes the convexed faces of the rotor blades and a considerable loss of )ower must necessarily result. In view of t is fact, it is to be nnderstood that the real purpose of reversing the direction in which the motive fluid strikes the rotor blades is to provide a means that shall effectively act as a brake, rather than that the turbine shall be operated in either direction of rotation. The need of such a braking means is more apparent when the fact is brought to mind that were the load to be taken off the tool while driving in the normal direction of rotation and then the motive fluid entirely shut ofi", the turbine would continue to run at a high rate of' speed for a considerable length of time, so well balanced are the several parts. Under such circumstances it would be impractical to stop the rotation of the turbine by the ap- `plication of a frictional braking means,

owing to the excessive wear that would rcsult, nor would it be practical to attempt to stop its rotation by grasping the end of the spindle or tool with the hand because ot' the liability of injury.

.ln order to provide` means wherel'lv the lever 66 will be prevented from remaining in reversed position except lwhen pressure is applied to it by the operator, the following construction is preferably employed: The lever is provided with a projecting fnger 66 extending inwardly beyond the axis of the valve member and moving within a narrow semicircular shaped recess 67 (Fig. 7) formed in the casing. Communicating with the upper end of said recess is a vertically arranged, cylindricaly bore 68 opening vagainst the bottom face of the hase plate 9 the tool handle 9. lVithin this bore is mounted an cndwise movable plunger (S9 provided with a central depression within which is retained a coiled spring 70. The spring' bears against the said base plate fr* of the tool handle and acts to constantly` force the plunger downwardly. A shoulder 68 formed at the'hottom of the bore 68 limits the downward movement of the plunger. In the closed position of the lever 6G, the finger 66 is in contact with the plunger in its extreme downward position. 'lhus the plunger normally acts as a stop for the lever at the closed position thereof. llowever, if it is desired to stop the rotationvof the turbine, the lever is forced downwardly against the pressure of the plunger to the reverse position, and remains in that. position until the lever is released by the oper ator, in which case the plunger acts upon the finger 66 forcing the lever to the closed position. To move the lever to the open position, the same is swung upwardly to approximately a vertical position, the linger at the same time moving downwardly and free from contact with the plunger 69. .X stop pin 71 is preferably provided at the lower extremity of the recess and engages the finger 66 of the lever at the open position of the same. lt is to he understood that the handle may be replaced b v a breast plate or a feed screw mechanism for bracing the tool if desired.

By the construction of a turbine as herein before described, several important features are disclosed which add greatly to the practical use of tools of' this type. One ofl such features is the introduction of the planctanvY form of power transmission embracing the spindle and the reduction gearing carried by the saine. lt is to be noted thatI the entire spindle is arranged in a synnnctrical mannism is obtained, whereby the highest pos-` tion ,is that the rotor is perfectlyl balanced ner about the turbine shaft, that is to say, i

the gears are all arranged in pairs located diametrically opposite each other on either side of the turbine shaft, the weight of. one acting to eounterbalance the weight of the other, and in like manner the driving effort of the turbine'shaft is transmitted to the spindle at two diametrically opposite points. The obvious advantage of this construction' is that a perfectly balanced mechaden jars or shocks such as are often experienced in the o eration of tools of this class and which wou d be injurious to the parts rotating at a high rate of speed. The high rate of speed at which the turbine shaft is lcapable of rotating in my device is largely due tothe arrangement of the nozzles 57 in that they are not only spaced about the circumference ofthe casing but that the air strikes the lblades at a tangent to the circumference of the rotor and not from the side as is often the arrangement in turbines of this class. Theadvantage of this construcin all directions so that there is no tendency for the turbine shaft to be shifted laterally or endwise so as to increase the friction and consequently vdecrease the speed obtainable. The arrangement of the two setsof nozzles, 011e of which directs the air against the turbine blades in a direction to reverse the normal direction of rotation, is a feature which permits the utilization of air as a brake to stop the rotor. One advantage of this form of brake is that it eliminates the use of all frictional brake devices which are objectionable in that a replacement of lthe arts is frequently required on 4account o the wear. Numerous other features lare embodied in my invention, all vof which combine to malte thedevi'ce a very'compact, ellicient and serviceable tool for drilling or like purposes.

I am aware that the construction of my device may be variously modified in its details without departing from the spirit of my invention, and for. that reason do not wish to be limitedto the structureherein. described or illustrated in the accompanying drawings,l except in so far as itis specifi-- cally set forth'in the appended claims.

I claim as my invention L'In a pneumatic turbine drill, the combination-of a casing, a rotor, a rotor shaft provided with a pinion, a tool spindle surrounding said rotor shaft and supporting one end thereof, a rotary gear wheel carried by said tool spindle and meshing with said rotor shaft pinion, a fixed gear, a pinion carried by said tool spindle and meshing with said fixed gear, and means for operatively connecting said lastfmentioned pinion with said rotary gear.

2. In a pneumatic turbine drill, the combination of a rotor, a rotor shaft provided with a pinion, a rotative tool s indle in axial alinement with said rotor sha t and forming a support for one end of said rotor shaft, a rotar gear Wheel carried by said tool spin le and .in toothed engagement with said rotor shaft pinion, a fixed gear, a pinion carried by said tool spindle and in toothed engagement with said fixed gear, and intermeshing gear members operatively connecting said rotary gearwheel with the pinion carried by said tool spindle. t I

l3. In a pneumatic turbine drill, the combination of a casing provided with a rotoi chamber, a rotor mounted within said rotor chambena gear casing, a rotor shaft, a tool spindle rotatively mounted in said gear casing, and forming a bearing for one eX- tremity of said rotor shaft, an annular disk separating said rotor chamber and gear casing, a bearing on said disk and in engagement with the rotor shaft, and speed reducing gearing carried by said tool spindle and in engagement with said rotor shaft and with said tool spindle. l

fl. In a pneumatic turbine drill, the comhina-tion of .a rotor casing, a rotor in said rotor casing, a gear casing, a spindle bearing supporting member, a rotor shaft extendingv through said supporting member and into said gear casing, a tool spindle in said gear casing surrounding the portion of said rotor'shaft Within the gear casing, a pinion on said rotor shaft, a rotor shaft bearing supported by said tool spindle, la fixed gear mounted in saidgear casing, and speed reducing gearing carried by said tool spindle and in driving engagement with said rotor shaft pinion und said fixed `gear.

bearing supported by the tool spindle and in engagement With one extremity of said rotor shaft, an internal gear fixed to said easing,- a rotary gear Wheel carried by said tool spindle and meshing' with the rotor shaft pinion, a pinion turning with said rotary gear Wheel, a second gear wheel carried by said tool 'spindle and meshing with the 'said last-mentioned pinion and provided with a pinion in toothed engagement with said internal gear.

6. In a pneumatic turbine drill, the combination of a rotor casing, a rotor mounted within said rotor casing, a gear casing, an annular disk separating said rotor and gear easings, a rotor shaft, extending through said annular disk and provided with a pinion, a tool spindle rotatively mounted in said gear easing, and comprislng tWo spindle disks one of said disks being provided with a bearing flange surrounding said rotor shaft, a bearing supported in said annular disk and engaging the said bearing fiange, the other of said spindle disks supporting a bearing for said rotor shaft, a spindle sleeve integral with said last mentioned disk and extending through said gear easing, an internal gear fixed in said gear easing, and speed reducing gearing carried by said tool spindle and in driving engagement with said rotor shaft pinion and said internal gear.

7. In a pneumatic turbine drill, the combination of a rotor easing, a rotor in said rotor casing, a gear easing, a fixed bearing supporting member intermediate said rotor and gear easings, a rotor shaft extending through said fixed bearing supporting member and into said gear easing, a tool spindle mounted in said gear easing comprising two transverse spindle members, a pinion on said rotor shaft, a rotor shaft bearing sup ported by one of the transverse spindle members, a fixed gear mounted in said gear easing, and speed reducing gearing carried b v said tool spindle and located between and supported bythe transverse spindle members. and in engagement with said rotor shaft pinion and said fixed gear.

H. In a. pneumatic turbine drill, the combination of a casing, a rotor, a rotor shaft provided with a pinion, an internal gear yfixed to said easing, a tool spindle, a gear wheel carried by the tool spindle and meshing with the rotor shaft pinion, a pinion integral with said gear wheel, a gear wheel meshing with the said last mentioned pinion, and a shaft integral with said last men tioned gear wheel and provided at its` end with a pinion meshing with said internal gear.

9. In a pneumaticl turbine drill, the rombination of a rotor, a rotor shaft provided with a pinion, a tool spindle in axial alinement with the rotor shaft, an internal gear fixed to said easing, a plurality of pairs of diametrieally opposed gear wheels carried b v said tool spindle, each of said gear wheels being provided with a pinion in axial alinement and turning therewith. one of said pairs of gear wheels meshing with the rotor shaft pinion, the other pair of gear wheels meshing with the pinions of the first mentioned pair of gear wheels, and the pinions of said last mentioned pair of gear wheels meshing with the said internal gear.

10. In a pneumatic turbine drill, the combination of a casing, a rotor, an internal gear fixed to said casing, a rotor shaft provided with a pinion, a tool spindle compris ing `two spindle disks secured in fixed relation, a gear wheel mounted between said spindle disks and meshing with the rotor shaft pinion, a. pinion fixed to said gear wheel, a gear Wheel located between said disks and meshing with said last mentioned pinion, a shaft fixed to said last mentioned gear wheel and extending through one of said spindle disks, and a pinion on said shaft and in toothed engagement with said internal gear.

11. In a pneumatic turbine drill, the combination of a easing, a rotor, an internal gear fixed to said easing, a rotor shaft provided with a pinion, a tool spindle comprising two spindle disks secured in fixed relation, a gear wheel mounted between said spindle disks and meshing with the rotor shaft pinion, a pinion fixedto said gear wheel, a gear wheel located between said disks and meshing with said last mentioned pinion. a shaft fixed to said last mentioned gear wheel and extending through one of said spindle disks. a pinion on vsaid shaft and in toothed engagement' with said internal gear, and a spindle sleeve fixed to one of: said .spindle disks and extending through the wall ofE the casing.

12. In a pneinnatir turbine drill, the combination of a rotor, a rotor shaft provided with a pinion, a tool spindle in axial alinement with the rotor shaft. an internal gear fixed `to said casing, a pair of gearwheels carried by said tool spindle and meshing with the rotor shaft pinion at diametrically opposite points. each of said gear wheels being provided with a pinion in axial alinement and turning therewith, and gearing interposed between said pinions of the gear wheels and said internal gear.

18. In a pneumatic turbine drill, the combination of a casing, a rotor, a rotor shaft. provided with a pinion, an internal gear fixed to saidvcasing, and a tool spindle comprising two transverse spindle members in axial alinement with the rotor shaft, a gear wheel mounted between said transverse spindle members and provided with a stub shaft, a pinion at the end of said stub shaft meshing with said internal gear, and driving means interposed between and operatively connected with said gear wheel and the pinion of the rotor shaft.

14. In a pneumatic turbine drill, the combination of a easing, a rotor, a rotor shaft provided with a pinion, a tool spindle eom- )rising two spindle disks secured in fixed re lation to each other, a plurality of pairs of gear spindles mounted in said spindle disks,

one of said pairs of gear spindles being provided with Gear wheels and pinions located between saidD disks, said gear Wheels meshing with the rotor shaft pinion at points thereof diametrica-lly opposlte, the other pair ot' gear spindles having projecting end portions extending through oneof said spindle disks and being providedvwith gear Wheels located between said spindle disks and meshing with the pinions of the first mentioned pair of gear spindles, and pinions at the extremities of the last mentioned pair of gear spindles and located beyond the disk through which said projecting gear spindles extend, and an internal gear fixed to said casing and in toothed engagement with the pinions of the last mentioned pair of gear spindles.

15. In a neuinatic turbine drill, the combination ot a casing, a rotor provided with radially extending blades or buckets, a channel surrounding said rotor, a nozzle communicating with said channel and the casing, said nozzle being adapted to directthe motive lluid against the said'buckets, and a plurality of annularly arranged exhaust openings in the wall of the casing located at either side of the channel.

16. In a pneumatic turbine drill, the combinationof a casing, a rotor provided at its periphery with radially extending blades, a plurality of nozzles lying in the plane of said rotor, said nozzles being oppositely inclined with respect to the axis of said rotor and adapted to direct the motive fluid against the said blades to eliect the rotation of the rotor in either direction, and a series of annularly arranged exhaust openings in the wall of the casing and located at either side of the plane of the rotor.

17. In a pneumatic turbine drill, the coinbinationfot a casing, a rotor provided at its periphery with radially extending blades, a plurality of nozalesv formed in said casing and lying in the plane et' said rotor, said nozzles being oppositely inclined to the axis of said rotor to direct the motive fluid against the said blades to el'ect the rotation of the rotor in either direction, a throttle valve for controlling the flow of the motive fluid into either of said nozzles, and means acting on said throttle valve to prevent the flow of the motive fluid into one of said channels, except when a constant pressure is applied to said throttle valve.

1S. ln a pneumatic turbine drill, the coinbination of a casing, a rotor provided at its periphery with radially extending blades, a plurality ot' channels formed in said casing surrounding said rotor, a partition wall separating said channels, a plurality of nozzles formed in said partition wall and communicating with said channels and the interior ot' the casing, said nozzles communieating with each of said channels being oppositely inclined to the axis of said rotor, to

direct the flow of the motive fluid against opposite faces of the said rotor blades, and aV throttle valve adapted to control the ilow of thl motive fluid to either of said air channe s.

19,. In a pneumatic turbine drill, the combination of a casing, a'rotor Within said casing provided with a plurality of blades, a plurality of annular channels surrounding said rotor, a plurality of nozzles communieating with each of said channels, the said nozzles communicating with one of the channels being similarly inclined 't'o the axis of the rotor to direct the motive fluid against the rearward sur-faces of the blades, for driving the rotor in one direction, and the nozzles communicating with the other of said channels being oppositely inclined with respect to the axis of the rotor-and adapted to direct the motive fluid against the opposite surfaces oit' the blades, a throttle valve adapted to control the flow ofl motive fluid to the said channels, and provided with an operating lever, and means acting on said lever to prevent the flow of the motive iluid against the rearward surfaces of the blades except when pressure is being applied to the said operating lever. i

20. In a pneumatic turbine drill, the combination of a casing, a rotor within said casing provided at its periphery With radially extending blades, a plurality of an nular channels surrounding said rotor, a plu-4 rality of nozzles communicating with said channels to direct the motive fluid against the blades, the said nozzles communicating with one of the channels lying in the plane of the rotor and inclined at an angle' to the axis o f the rotor to effect the rotatlon of the rotor 1n one direction, and the nozzles communicating with the other of said channels also lying in a plane of the rotor and inclined at an angle to the axis of the rotor to effect the rotation of the rotor in the opposite direction, a manually operable throttle valve adapted to control the flow of motive fluid to the said channels, and means for preventing the flow into one of said channels except-when pressure is being applied to the said valve.

2l. In a pneumatic turbine drill, the combination of a rotor casing, a rotor provided with radially extending blades, a rotor shaft, a series of nozzles lying in the plane of the rotor and oppositely inclined to the axis of said rotor shaft and adapted to di rect the flow of the motive fluid to drive the rotor in either direction, means for controlling the flow oi' the motive fluid to either series of nozzles, and a plurality of' exhaust openings in said casing arranged in a plane parallel and adjacent to the plane of the rotor.

92. ln a pneumatic turbine drill, the combination of a rotor casing, a rotor provided with radiallyextending blades, a rotor shaft provided with a pinion, a Vseries of nozzles lying in the plane of the rotor and oppositely inclined with respect 'to the axis of said rotor shaft to direct the ow ofthe motive fluid to drive-the rotor in either direction, means for controlling the How of the motive fluid to either series of nozzles, a gear casing, an annular disk interposed between said rotor casing and said gear easing, a rotative tool spindle mounted 1n said gear casing, a fixed internal gear within said gear easing, a bearing for sald spindle supported 1n sald annular disk and said gear casing, bearings for said rotor shaft supported in said rotor easing and said tool spindle, and speed reducing gearing carried by said tool spindle and interposed between the internal gear and the rotor shaft pinion.

23. In a pneumatic turbine drill, the combination of a rotor casing, a rotor, a rotor shaft carrying said rotor and provided with a bearing in said rotor easing and a pinion, a gear easing, a rotative tool spindle mounted in said gear casing, a spindle bearing support secured between the adjacent margins of the said rotor and gear casings, a clamping ring engaging the margins of said rotor and gear casings, a bearing in said spindle for the rotor shaft, an internal gear fixed in said gear casing, and speed reducing gears carried by said spindle and in driving engagement with said internal gear and the pinion of the rotor shaft.

24. In a pneumatic turbine drill, the combination oi. a rotor easing, a rotor, a rotor shaft carrying said rotor and provided with a bearing in said rotor casing and a pinion, a gear casing, a rotative tool spindle mounted in said gear casing, an annular disk support mounted between the adjacent margins of the said rotor and gear casings, a spindle bearing supported in said disk, a clamping ring in screw-threaded engagement with the margins ol .said rotor and gear casings, a bearing in said spindle for the rotor shaft, an internal gear fixed in said gear casing, and speed reducing gears carried by said spindle and meshing with said internal gear and with the pinion of the rotor shaft.

25. In a pneumatic turbine drill,tbe combination of a rotor casing,a rotor, a rotor shaft carrying said rotor and provided with a bearing in said rotor easing and a pinion, a gear casing, a relative tool spindle in said gear casing, an annular disk mounted between said rotor casing and gear casing, and supporting a bearing for one end of said tool spindle, a thrust bearing mounted between said annular disk and tool spindle, a spindie sleeve integral with said spindle and extending tl'n'ough the wall of said gear casing, a [wearing engaging said sleeve, an internal gear fixed in said gear casing. and speed reducing gears` carried by said tool spindle and meshing with said internal gear and the pinion of the rotor shaft.

26. In a neumatic turbine drill, the combination o a rotor casing, a rotor, a rotor 4shaft carrying said rotor and provided with .bination of a easing, a rotor, a rotor shaft,

a tool spindle in axial. alinement with said rotor shaft and provided with a bearing for one extremity of said shaft, a sleeve integral with said spindle and extending through the wall of the casing, said sleeve having a eentral bore of uniform diameter provided upon its surface with a longitudinal projection, a tool-holding member fitting within said bore and provided with a longitudinal groove adapted t0 engage said lug of the spindle sleeve and a lock nut in screwt readed engagement with the end of said spindle sleeve and bearing against said socket sleeve to hold the same within the spindle sleeve.

28. In a power actuated drill, the combination of a easing, a rotor, a tool spindle mounted in the casing inoperative connection with the rotor, a sleeve integral with said tool spindle extending through the wall of the casing, said sleeve having an axial bore of uniform diameter provided upon its surfaces with a plurality of oppositely disposed, longitudinal projections, a tool-holding member fitting within the said bore and provided with longitudinal grooves adapted to be engaged by said projections, and with an annular flange abutting against the end of the sleeve, and a lock-nut having screwthreaded engagement with the end of the sleeve and bearing against the said lock-nut.

29. In a pneumatic turbine drill, the eombination of a casing, a rotor provided with radially extending "blades, a plurality of passages surrounding said rotor lying in the plane of the rotor and inclined at an angle to the axis thereof, said assages being adapted to direct the motive f uid against one face of the blades to drive the rotor in a direction for the normal operation of the tool, and a brake comprisingr a passage adapted to direct the motive fluid against the opposite face of the said blades, a throttle valve for controlling the flow of the motive fluid to such passages, and means acting on said throttle valve to prevent the flow of the motive fluid against said opposite face of the blade except when a constant pressure is applied to said throttle valve.

30. In a pneumatic turbine drill, the combination of a casing, a rotor provided with radially extending blades, a plurality of passages surrounding said rotor lying in the plane of the -rotor and inclined at an angle to the axis thereof, said passages being adapt-ed to direct the motive fluid against one face of the blades to drive the rotor in a direction for the normal operation of the tool, and a brake 'comprising a passage adapted to direct the motive fluid against the opposite face of the said blades, a throttle valve for controlling the How of the motive fluid to said passages, and means acting on said valve to prevent the flow of the motive uid to said last mentioned passage eX- A cept when a constant pressure is being applied to the lever of said valve.

31. Ina pneumatic turbine drill, the combination of a casing, a rotor mounted in said casing and provided at its periphery with a plurality of radially extending blades, a plu rality of channels comprising vgrooves formed in said casing and surrounding said rotor, said grooves being separated by an annular partition Wall, and a ring surrounding said casing and said grooves, a series of nozzles formed in said partition Wall and communicating with each of said channels,

each of said series of nozzles being oppositely inclined atan angle to the 'axis of the rotor to direct the flow of the motive fluid to rotate the rotor in opposite directions, and a throttle valve for controllinvr the liovv of the motive fluid in said channe s.

32. In a pneumatic turbine drill, the combination of a casing, a rotor provided with radially extending blades, a plurality or series of nozzles in said casing, said series of nozzles being oppositely inclined at angles to the axis of the rotor to direct the loWzof the motive fluid to rotate the said rotor in either direction, 'passages communicating With said series of nozzles, and a throttle valve interposed between said passages and the source of su ply and comprising a movable valve ,mem er, a throttle lever, and a spring actuatingplunger acting on said throttle lever to prevent the continued flow of the motive fluid to one of said passages except when a constant pressure is applied to the throttle lever.

In testimony, that I, claim the foregoing as my invention I aiiiX my si ature in the presence of two Witnesses, this-4th day of September, A. D. 1913.

REINHOLD A. NORLING.

Witnesses:

C. S. MooNEY, M. JfBURKEL. 

